JP2022554406A - pericyclic transmission - Google Patents

Abstract

at least one input shaft (58) rotatable about an axis of rotation and at least one tilted bearing seat (55, 56) fixed to the input shaft, the tilted bearing seat pericyclic transmission oriented at an oblique angle with respect to the axis of rotation of the The input gears (52, 54) are mounted on each tilted bearing seat with the input gears oriented at the tilt angle and having their axes of rotation tilted by the tilt angle with respect to the axis of rotation of the input shafts. , whereby the input gear performs at least a nutation motion upon rotation of the input shaft. The transmission also includes intermediate gears (51, 53) meshing with the input gear, the intermediate gears having an axis of rotation coinciding with the axis of rotation of the input shaft. The intermediate gear communicates with the transmission output.

Description

The present invention is particularly directed to pericyclic transmissions that offset unbalanced moments or forces with a reduced number of gears versus state-of-the-art solutions by providing different output configurations.

FIG. 1 shows two ring gears 10 and 11 meshing together in zone 15 . Tooth 1 and slot 1 are shown in the fully engaged position. The number of teeth of gear 10 and gear 11 differ by only one or two. The angle 14 between the input shaft 12 and the output shaft 13 is slightly less than 180°. The two gears 10 and 11 have a conventional arrangement (not pericyclic) but are the basic elements of the pericyclic transmission.

A pericyclic transmission consists of 4 to 8 bevel gears. Each pair of bevel gears has a shaft angle close to 180°. The number of teeth of each pair of meshing bevel gears differs by one or two. FIG. 1 shows a gear pair with approximately the same number of teeth and an axial angle 14 close to 180° in a conventional arrangement (not pericyclic). Pericyclic transmissions use two to four bevel gear pairs as basic elements, such as the one shown in FIG. Introduce exercise.

As shown in FIG. 1, the smallest possible axial angle difference to 180° of the meshing bevel gears is defined by the total tooth depth. In order for the teeth to engage only in one zone 15 of the circumference and disengage in the opposite zone 16, the axial angle is at least 180°-arctan {[(hole depth)*2+clearance]/( outer cone distance)}.

The amount of clearance 17 should be about 50% or more of the total tooth depth to allow meshing between the two meshing gears. The meshing conditions are different from the standard bevel gear ratio 1-5. Due to the nearly 180° shaft angle there is a large engagement zone 15 between the meshing teeth. The size of the angle of engagement zone is usually chosen to be less than 90°, since a difference of one or two teeth between the meshing gears causes one of the two gears to rotate faster. This is the case if the first gear 10 has one tooth more than the second gear 11 and if the second gear tooth no. 1 is the slot number of the first gear. 1, tooth no. 1 disengages at the end of the engagement zone and enters the other end of the engagement zone while engaging slot No. 1 of the first gear. 2 through one tooth of the first gear to then re-engage. The process of disengagement, passage of one tooth and re-engagement with the next slot not only requires sufficient clearance between the tips of the meshing teeth, but also allows passage of one tooth without interference. For this purpose, a sufficient angle of the disengagement zone is also required.

If the first gear 10 and the second gear 11 are connected to separate shafts (12 and 13) and have a shaft angle of less than 180°, as shown in FIG. It becomes the number of teeth of the second gear 11 divided by the number of teeth 10 (z ₂ /z ₁ ). For z ₁ =40 and z ₂ =41, the ratio is commonly expressed as 40×41 or 0.9756.

In a pericyclic transmission, bevel gear pairs with a shaft angle of approximately 180° are utilized differently than shown in FIG. FIG. 2 shows gear 20 meshing with gear 21 in zone 22 . Gear 21 is rigidly connected (or integral) with gear 23 , which meshes with gear 24 in zone 19 . The axial angle between gears 20 and 21 is indicated by 26 and the axial angle between gears 23 and 24 is indicated by 27 . To give pericyclic functionality to the transmission in FIG. Nutating gears 21 and 22 have bearings on angled shaft section 30 such that the pitch lines of gears 20, 21, 23 and 24 all intersect at point 50 which is also the intersection of axes 29 and 33. must be placed The bearings allow nutation gears 21 and 23 to rotate freely on angled shaft 30 so that contact zones 22 and 19 (with a rotational offset angle of 180°) are aligned with gears 20 and 24. rotate around the circumference of This oscillating motion has a frequency of the input RPM. However, gears 21 and 23 only rotate one or two angular pitches per rocking rotation, depending on the number of tooth combinations between gears 20 and 21 . The number of tooth combinations between gears 23 and 24 must be different than between gears 21 and 20 to achieve an output rotation 32 different from zero (using the ratio calculation below see).

Ratio calculations for pericyclic transmissions differ significantly from typical ratio calculations for gear transmissions. The calculation is illustrated in the following example:
Number of teeth Gear 20: z ₂₀ = 40
Number of teeth Gear 21: z ₂₁ = 41
Number of teeth Gear 23: z ₂₃ = 61
Number of teeth Gear 24: z ₂₄ = 60

The calculation begins with the constrained gear and its mating partner, in FIG. 2 the gear 20 which is rigidly connected to the gearbox housing 31 and thus constrained, and the first gear meshing with the constrained gear. , and the gear 21 . In a pericyclic transmission, an input rotation rotates a tilted central shaft 30 holding gears 21 and 23 through bearings (no positive torque connection). When the input rotation 28 rotates the input shaft 29, which is connected to the inclined shaft section 30, then instead of substantially the same high speed rotation of the gears 21 and 23, only nutating or oscillating motion occurs. Each nutation of tilted shaft 30 moves gear 21 (and connected gear 23) one pitch backward based on the angular pitch of gear 21 (Δφ ₁ =−360°/41=−8.7805°). will rotate to A chaptering motion between gears 23 and 24 will rotate gear 24 forward one pitch, based on the pitch of gear 23 (Δφ ₂ =360°/60=6.0°). This means that output shaft 32 rotates Δφ ₁ +Δφ ₂ =−2.7805° for each full rotation of input shaft 28 . The ratio of this pericyclic transmission is i _pericyclic =360°/(−2.7805°)=−129.47368. This ratio calculation follows the rules:
Based on ω _output = ω _input /i _pericyclic .

Another notation for ratio calculations is:
i _pericyclic =[(z _constrained -z _{first unconstrained} )/z _{first unconstrained} +(z _{indirectly constrained} -z _{second unconstrained} )/z _{indirectly constrained} ] ^-1 ,
In the formula:

A transmission such as that shown in FIG. 2 (see, for example, Lemanski US Pat. Generate. The rotation of gears 21 and 23 is slow compared to the input RPM (RPM _21/23 =RPM _input /i _pericyclic ), but the nutation-oscillating motion is fast and has the same frequency (1/min) as the input RPM. . The nutating oscillating motion causes a fluctuating moment about axis 50 that acts on gearbox housing 31 to alternate between clockwise (cw) direction 26 and counterclockwise (ccw) direction 27 . Structural vibration caused by imbalance is not acceptable for all applications with input speeds above about 100 RPM.

Cutting-edge removal of imbalance is achieved by connecting a second mirror-image pericyclic unit to the first pericyclic unit, as shown in FIG. Pericyclic Transmission Prototype: Detailed Component Design, Analysis and Fabrication", AHS-The Vertical Flight Society, May 2019). Gear 40 equals gear 24 , gear 41 equals gear 23 , gear 43 equals gear 21 and gear 42 equals gear 20 . Output gear 34 is positioned between gear 24 and gear 40 and is rigidly connected. Input shaft 29 is rigidly connected to shaft sections 30 , 33 , 35 and 44 . The reaction members (gears 20 and 42) are connected to the gearbox housing 31 and therefore cannot rotate. Input rotation 28 is transferred to output 45, where output 45 has a reduced rotation speed.

The two units in FIG. 3 are connected to output gear 34 . Gear 40 is a mirror image of gear 24 . Gear pairs 41 and 43 are mirror images of gear pairs 21 and 23 and gear 42 is a mirror image of gear 20 . Gear 42 , like gear 20 , is rigidly connected to gearbox housing 31 . The shaft sections 29, 30, 33, 35 and 44 are rigidly connected like one solid part. The nutation-oscillation motions of the two intermediate gear pairs 21 and 23 and 41 and 43 in FIG. 3 have opposite directions, leading to complete cancellation of system-related imbalances. Output gear 34 is rigidly connected to gear 24 and gear 40 . The ratio between the input shaft 29 and the output gear 34 is the same as that of the transmission in FIG.

Significant drawbacks of state-of-the-art solutions include the fact that the number of gears required to balance the pericyclic transmission must be doubled. Also, the size of the transmission is increased to approximately double the size of the transmission shown in FIG. Another drawback is the central location of the output gear 34 which requires an additional gear to mesh with gear 34 to provide a rotating output shaft.

The present invention is directed to pericyclic transmissions that offset unbalanced moments or forces with reduced gear count versus state-of-the-art solutions by providing different output configurations.

The pericyclic transmission comprises at least one input shaft rotatable about an axis of rotation and at least one tilted bearing seat fixed to the input shaft, the tilted bearing seat being aligned with the input shaft's axis of rotation. oriented at an oblique angle with respect to The input gear is mounted on each tilted bearing seat with the input gear oriented at the tilt angle and having its axis of rotation tilted by the tilt angle with respect to the axis of rotation of the input shaft, whereby Upon rotation of the input shaft, the input gear performs at least nutation motion. The transmission also includes an intermediate gear meshing with the input gear, the intermediate gear having an axis of rotation coinciding with the axis of rotation of the input shaft. The intermediate gear communicates with the transmission output.

FIG. 1 illustrates two ring gears with one tooth difference. FIG. 2 shows a conventional pericyclic transmission. FIG. 3 shows a conventional balanced pericyclic transmission. FIG. 4 illustrates a reverse pericyclic transmission output through the side of the transmission housing. FIG. 5 illustrates a reverse pericyclic transmission in which the input and output shafts are in line. FIG. 6 shows advanced reverse pericyclic transmission. FIG. 7 shows separation of the two nutation members of FIG. Figure 8 illustrates the nutation member of Figure 7 after changing the input and output shafts after rotation. FIG. 9 shows the placement of the electric motor between the two transmission halves of FIG. FIG. 10 shows a transmission unit connected with a differential shaft and an idler. FIG. 11 illustrates additional couplings and clutches for torque vectoring and traction control. FIG. 12 shows a dual motor arrangement.

As used herein, the terms "invention," "the invention," and "the present invention" refer to all of the subject matter of this specification and to any It is intended to refer broadly to the claims. Statements containing these terms should not be taken to limit the subject matter described herein or to limit the meaning or scope of any of the following claims. Furthermore, the specification does not attempt to describe or limit the subject matter covered by any claim in any particular part, paragraph, statement, or drawing of this application. The present subject matter should be understood by reference to the entire specification, all drawings, and any of the following claims. The invention is capable of other configurations and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting.

Details of the invention will now be discussed, by way of example only, with reference to the accompanying drawings which illustrate the invention. In the drawings, similar features or components are referred to by similar reference numerals. The sizes and relative sizes of certain aspects or elements may be exaggerated for clarity or for illustrative purposes. Doors, casings, inner or outer guards, etc. may be omitted from the drawings for better understanding and clarity of the invention.

The use of "including," "having," and "comprising" and variations thereof herein is meant to encompass the items listed thereafter and their equivalents, as well as additional items. As used herein, the singular forms "a," "an," and "the" refer to the plural as well, unless the context clearly indicates otherwise. and the term "and/or" includes any and all combinations of one or more of the associated listed items.

Hereinafter, when describing the drawings, directions such as top, bottom, upward, downward, rearward, bottom, top, front, rear, etc. may be referred to for convenience. are mentioned). These directions are not intended to be taken literally or to limit the invention in any way. Additionally, terms such as “first,” “second,” “third,” and the like are used herein for the purpose of description and unless explicitly stated otherwise, have no significance or significance. is not intended to indicate or imply

A first embodiment of the solution of the invention, shown in FIG. 4, reverses the concept of FIG. consists of two identical gears, preferably straight bevel ring gears, oriented back-to-back and having cylindrical gears with teeth 59 located on their periphery. Gears 51 and 53 can be manufactured by non-generating or generating methods. A cylindrical gear 59 on the outer periphery of gear pairs 51 and 53 is the pericyclic transmission output. Pericyclic motion occurs between gears 52 and 51 and between gears 52 and 51 as input shaft 58 rotates angled bearing seats 55 and 56 about their respective axes that are tilted with respect to the axis of rotation of input shaft 58. This is achieved by tooth engagement between 54 and gear 53 . The engagement zone of the teeth rotates around the circumference of input gears 52 and 54 while gears 52 and 54 oscillate without rotation.

Input gears 52 and 54 are preferably identical internal gears, preferably straight internal non-generating bevel gears mounted in a mirror image orientation, and carry out nutating motion initiated by inclined bearing seats 55 and 56. do. Alternatively, the internal gear can be an internal gear, or the internal gear can have curved teeth. Gears 52 and 54 are restrained from rotating by swing pins 61 and 62 engaged in slots 63 and 64 inside transmission housing 60 . Input shaft 58 is rigidly connected to shaft sections 55 , 57 , 56 and 65 . This arrangement results in gears 52 and 54 being the nutation reaction gears and gears 51, 53 and 59 being the slow rotating output units. Input shaft 58 and sections 55, 57 and 56 and 65 may be formed from a single piece of material (eg, steel).

For example, if input gears 52 and 54 have 41 teeth and intermediate gears 51 and 53 have 40 teeth, each rotation of input shaft 58 nutates (i.e., oscillates) while input gear 52 and 54 are not rotated, thereby rotating the intermediate gear pair 51, 53 by one pitch in the negative direction. Preferably, the difference in the number of teeth of the input gear and the meshing intermediate gear is in the range of 1-5, more preferably 1 or 2.

Rotation is transmitted via cylindrical gear 59 to a second cylindrical gear outside transmission housing 60 which is mounted on an output shaft (not shown). If the input shaft 58 rotates 40 times, the gear 59 rotates forward one revolution (ratio i _pericyclic =[1/40] ⁻¹ =40).
i _pericyclic = [(z _constrained - z _{1st unconstrained} )/z _{1st unconstrained} ] ^-1
i _pericyclic = [(z ₅₂ - z ₅₁ )/z ₅₁ ] ^-1 = [(z ₅₃ - z ₅₄ )/z ₅₄ ] ^-1 = [(41 - 40)/40] ^-1 = 40

Another embodiment of the invention having an output shaft 87 in line with the input shaft 78 is shown in FIG. The concept of FIG. 5 also inverts that of FIG. 2 by using a centrally mounted intermediate gear pair 71 and 73 . Intermediate gear pairs 71 and 73 are connected to gearbox housing 70, while gears 72 and 74 perform a nutating motion initiated by tilted bearing seats 75 and 76. Intermediate gear pairs 71 and 73 are identical gears oriented back-to-back in one unit. Nutation gears 72 and 74 are also identical, but mounted in a mirror image orientation. One revolution of the input shaft 78 rotates the two angled bearing seats 75 and 76 and rotates the gears 72 and 74 by one or two angled tooth pitches (depending on the gear ratio); Achieve one complete nutation. This rotation is transmitted to pin 80 through slots 83 and 85 and to pin 81 through slots 84 and 86 . Pins 80 and 81 transmit rotation to output tube 87 and integral flange 82 .

Input shaft 78 is rigidly connected to shaft sections 75 , 77 , 76 and 79 . For example, if gears 72 and 74 each have 41 teeth and gears 71 and 73 each have 40 teeth, each rotation of input shaft 78 causes gears 72 and 74 to rotate one pitch. Rotation is transmitted to flange 82 of output tube 87 via pins 80 and 81 . When the input shaft 78 rotates 41 times, the output tube 87 rotates backward one revolution (ratio i _pericyclic =-41).
i _pericyclic = [(z _constrained - z _{1st unconstrained} )/z _{1st unconstrained} ] ^-1
i _pericyclic =[( _z71 - _z72 )/ _z72 ] ^-1 =[( _z73 - _z74 )/ _z74 ] ^-1 =[(40-41)/41] ^-1 =-41

A preferred embodiment of the invention is shown in FIG. 6, which also reverses the concept of FIG. 2 by using a centrally mounted intermediate gear pair 91 and 93. Intermediate gear pairs 91 and 93 are connected to gearbox housing 90, while gears 92 and 94 perform nutation initiated by slanted bearing seats 95 and 96. Gears 92 and 94 engage intermediate gears 91 and 93 and their outer halves 102 and 103 of their face widths, which are reaction members. Input shaft 98 is rigidly connected to shaft sections 95 , 97 , 96 and 99 . If gears 92 and 94 perform one nutating rotation, then they both rotate by one or two angled tooth pitches (depending on the gear ratio). For example, if gears 92 and 94 have 41 teeth and gears 91 and 93 have 40 teeth, each rotation of input shaft 98 causes gears 92 and 94 to rotate one pitch.

In FIG. 6, the rotation of gears 92 and 94 is transmitted to the output shaft via centrally mounted transfer gear pair 104 and 105 and to flange 112 and output shaft 106 via transfer pins 100 and 101 . Transfer gear pair 104 and 105 are centrally positioned relative to axis 97 and are freely rotatable about axis 97 with teeth engaging inner halves 107 and 108 of the face width of gears 92 and 94. be. The number of teeth between gears 92 and 104 and between gears 94 and 105 are the same, which through transfer pins 100 and 101 is the precise rotational component of the motion of gears 92 and 94. (excluding the nutation-swing component) to the flange 112 and, in turn, the output shaft 106. If the input shaft 98 rotates 40 times, the output shaft 106 rotates backward one revolution (ratio i _pericyclic =−41).
i _pericyclic = [(z _constrained - z _{1st unconstrained} )/z _{1st unconstrained} ] ^-1
i _pericyclic =[(z ₉₁ -z ₁₀₂ )/z ₁₀₂ ] ⁻¹ =[(z ₉₃ −z ₁₀₃ )/z ₁₀₃ ] ⁻¹ =[(40−41)/41] ⁻¹ =−41

Holes 109 and 110 provide a sufficient amount of clearance for transfer pins 100 and 101 while gear pair 104/105 rotates in mesh with gears 92 and 94. To maintain clearance between pins 100 and 101 and between holes 109 and 110, the number of teeth on gears 92 and 104 and 94 and 105 should be the same.

Below are some application examples for electric vehicle drives.

Electric vehicles are propelled with high speed electric motors. These electric motors operate at RPMs that are three to five times higher than those of internal combustion engines. The requirements for reduction transmissions with very high ratios between the electric motor and the drive wheels are therefore evident. Pericyclic transmissions achieve the required high ratios and also score flank surfaces due to the fact that the relative motion between meshing teeth is considerably lower compared to conventional high speed cylindrical gearboxes. allow high input speeds without the risk of

A compact solution is required when the drive unit with motor and transmission has to fit between the drive wheels. The power density and compact layout of the inventive transmission examples of FIGS. 4, 5 and 6 appear to be well suited for the deceleration task of electric vehicles. One requirement of the final drive unit is an output shaft on each side of the transmission. The drive shaft to the wheels must be connected to the output shaft (or output flange).

FIG. 7 shows the transmission of FIG. 6 cut vertically in two halves in the center. After separating the two nutation members, each half is rotated 180° about the vertical axis. The result of this rotation is shown in FIG. Also, the input and output shafts are reversed so that the electric motor can be installed between the two units and the drive shaft to the wheels can be connected on the outside of the two units. .

FIG. 9 shows an arrangement involving the installation of electric motor 140 between the two transmission units of FIG. The unit of Figure 9 does not have a differential function. This function is required when the vehicle drives through curves and the outer wheels drive a longer distance (have to turn faster) than the inner wheels.

The embodiment shown in Figure 10 solves the task of differential function between the two output shafts 125, 126 by adding a connecting shaft with two pinions and an idler gear. Two reaction members 91 and 93 (FIG. 6) are not connected to the transmission housing, but have teeth formed on the outside and are numbered 120 and 121 . Gear 121 meshes with an idler pinion 122 that drives a pinion 123 on shaft 124 . Shaft 124 is rigidly connected to pinion 127 which meshes with gear 120 . Pinions 122, 123 and 127 have the same number of teeth. This arrangement acts like a differential between output shaft 125 and output shaft 126 . When a vehicle propelled by this unit drives through a curve, the speed of the vehicle remains constant, but when the axle 125 is connected to the wheels driving on the outside of the curve, it maintains the vehicle speed and 2 To accommodate the different arc lengths that the two drive wheels must travel while driving through a curve, shaft 125 rotates a certain amount faster than the motor RPM, and shaft 126 rotates the motor Rotate the same amount slower than the RPM.

FIG. 11 shows the addition of one coupling and two clutches for torque vectoring and traction control. A coupler 133 is installed between the two half shafts 131 and 132 . Additional clutches 134 and 135 may connect or disconnect shafts 131 and/or 132 to the transmission housing while coupling 133 is disengaged. This arrangement allows the amount of torque transmitted to output shafts 125 and 126 to be controlled. Such a function is called "torque vectoring" or "traction control".

If motor 140 is replaced by two separately controlled motors 141 and 142 (FIG. 12), torque vectoring via electronic control of the two motors can also be achieved. One side effect of this arrangement is that the two nutation gears change their angular phase relationship (if the first motor rotates faster than the second motor), which leads to a certain imbalance of the unit. It is a fact.

FIG. 12 shows a dual motor arrangement. By independently controlling each motor 141, 142, torque vectoring and traction control, respectively, can be achieved without the need for mechanical differentials.

Although the invention has been described with reference to preferred embodiments, it is to be understood that the invention is not limited to these specific embodiments. The present invention is intended to include modifications that will be apparent to those skilled in the art to which this subject belongs without departing from the spirit and scope of the appended claims.

Claims (20)

A pericyclic transmission,
at least one input shaft rotatable about an axis of rotation;
at least one slanted bearing seat fixed to said at least one input shaft, said at least one slanted bearing seat oriented at an oblique angle with respect to said axis of rotation of said at least one input shaft , at least one inclined bearing seat, and
an input gear mounted on each of said at least one tilted bearing seat, said input gear oriented at said tilt angle and said tilt with respect to said axis of rotation of said at least one input shaft; an input gear having an angularly inclined axis of rotation such that upon rotation of said at least one input shaft said input gear performs at least a nutating motion;
an intermediate gear meshing with the input gear, the intermediate gear having an axis of rotation coinciding with the axis of rotation of the at least one input shaft;
A pericyclic transmission, wherein said intermediate gear communicates with at least one transmission output. 2. The transmission of claim 1, wherein said input gear comprises an internal bevel gear or an internal surface gear. 3. The transmission of claim 2, wherein the inner bevel gear or inner side gear comprises straight teeth. 2. The transmission of claim 1, comprising two intermediate gears arranged back-to-back. 5. The transmission of claim 4, further comprising two input gears arranged opposite each other in a mirror image orientation. 6. The method of claim 5, wherein the two input gears are constrained from rotating about their respective axes of rotation and the two intermediate gears are rotatable about their respective axes of rotation. Transmission as described. 7. The transmission of claim 6, wherein said two intermediate gears include an outer circumference and further include a cylindrical gear formed on said outer circumference, said cylindrical gear being said transmission output. 6. The method of claim 5, wherein the two input gears are rotatable about their respective axes of rotation and the two intermediate gears are constrained from rotating about their respective axes of rotation. Transmission as described. 9. The transmission of claim 8, wherein rotation of said two input gears is transferred to said output via a plurality of transfer pins extending between said two input gears and said output. a pair of rotatable transfer gears concentrically disposed within the two restrained intermediate gears, wherein rotation of the two input gears extends between the pair of transfer gears and the output; is transmitted to the output through the transfer pin of
9. The transmission of claim 8, wherein said two input gears and said pair of transfer gears each have the same number of teeth. the input gear has a first number of teeth and the intermediate gear has a second number of teeth, the first number of teeth and the second number of teeth being one or two 2. The transmission of claim 1, wherein the transmission is different by one. a first input shaft rotatable about the rotation axis and a second input shaft rotatable about the rotation axis, wherein the first input shaft and the second input shaft are axially aligned with each other; aligned in a direction and positioned end-to-end,
2. The transmission of claim 1, wherein said transmission further comprises a first output associated with said first input shaft and a second output associated with said second input shaft. a first input gear and a second input gear, said first and second input gears being arranged back-to-back and axially spaced apart; 13. The transmission of Claim 12, wherein the gear is rotatable. further comprising a first intermediate gear and a second intermediate gear, wherein the first and second intermediate gears are arranged opposite each other in a mirror image orientation, the first and second intermediate gears are configured to rotate; 14. The transmission of claim 13, wherein the transmission is restrained. further comprising a first rotatable toothed flange integral with said first output and a second rotatable toothed flange integral with said second output, said first rotatable toothed flange , concentrically disposed within said first restrained intermediate gear, and said second rotatable toothed flange concentrically disposed within said second restrained intermediate gear; ,
The first rotatable toothed flange meshes with the first input gear and the second rotatable toothed flange meshes with the second input gear, thereby rotation of first and second input gears via said first rotatable toothed flange and said second rotatable toothed flange, respectively, to said first output and said second output, respectively; 15. Transmission according to claim 14. further comprising a motor connected to each of said first input shaft and said second input shaft, whereby rotation is imparted to each of said first input shaft and said second input shaft by said motor; 13. The transmission of claim 12, wherein: further comprising a first motor connected to the first input shaft and a second motor connected to the second input shaft, wherein the first motor and the second motor are separate 13. The transmission of claim 12, wherein the transmission is controllable to said first input shaft, said first input gear, said first intermediate gear and said first output form a first transmission portion;
said second input shaft, said second input gear, said second intermediate gear and said second output form a second transmission portion;
3. A motor is disposed between said first and second transmission portions, said motor being connected to each of said first input shaft and said second input shaft. 14. Transmission according to 14. a first intermediate gear and a second intermediate gear, wherein said first and second intermediate gears are arranged opposite each other in a mirror image orientation, said first and second intermediate gears being rotatable a first intermediate gear and a second intermediate gear, and
a differential mechanism connected to said first intermediate gear and said second intermediate gear thereby providing a differential function between said first output and said second output. 14. A transmission according to claim 13. 20. The differential mechanism of claim 19, further comprising a coupling and two clutches whereby the amount of torque transmitted to the first output and the second output is controllable. transmission.

Images